Transmission



Feb. 4, 1958 w BAKER 2,821,864

TRANSMISSION Original Filed Jan. 24, 1952 3 Sheets-Sheet 1 33 J A; /2 I J 5 1 22 5% J J i 53 5 2: 4 5/ i 37 X l/i s 2 24 HI 8 3 5 E1 E 4 2 INVENTOR.

' W/uA/Pp CBAKA-V? rro/e/vm Feb. 4, 1958 w. c. BAKER TRANSMISSION 3 Sheets-Sheet 2 Original Filed Jan. 24, 1952 I INVENTOR. I W/z A A/PD (784/052 Feb. 4, 1958 w. c. BAKER 2,821,864

TRANSMISSION Original Filed Jan. 24. 1952 3 Sheets-Sheet 3 INVENTQR. Wax/1 (3514mm TRANSMISSION Willard C. Baker, Plymouth, Mich., assignor to Jered Industries, Inc., Hazel Park, Mich., a corporation of Michigan Original application January 24, 1952, Serial No. 268,043, now Patent No. 2,687,652, dated August 31, 1954.

Divided and this application August 18, 1954, Serial No. 450,574

3 Claims. (Cl. 74-378) application, Serial No. 268,043, filed January 24, 1952,

which issued on August 31, 1954, as U. S. Patent No. 2,687,652.

The provision of a transmission of the type referred to above being a principal object of my invention, another object of my invention is to provide a means for reducing the gear teeth loads on the individual gears of the transmission.

A further object of my invention is to provide a power transmission of the type referred to above wherein the bearing loads caused by unbalanced separating forces for the individual transmission gears and by unbalanced tangential gear tooth forces are substantially eliminated.

A more specific objectof my invention is to provide a power transmitting mechanism for delivering power 2,821,364 Patented F eb. 4, 1958 In the presently disclosed embodiment of the invention, the power input pinion may be more conveniently mounted in the above-described n-ovel manner than any of the other gears. However, a mere matter of design would be required to so mount one or more of the other gears while the power input pinion is rotatably mounted in a fixed position.

In my copending application, above mentioned, I have disclosed a means for selectively clutching either of the intermediate gears to the cross shaft which is disposed perpendicularly to the power input shaft. The abovementioned intermediate gears function as power output gears in this instance, the above-mentioned power output gear and the de-clutched intermediate gear functioning as idler gears to provide a second power flow path from the input shaft to the output shaft.

For the purpose of more particularly describing my instant invention, reference will be made to the accompanying drawings wherein:

Figure 1 is a side view of the right angle drive transmission showing the outside of the housing;

Figure 2 is a horizontal sectional view of the transmission taken on the line 2-2 of Figure 1 with part shown in elevation;

Figure 3 is a vertical sectional view of the transmission taken on the line 3--3 of Figure 2 together with part Shown in elevation;

Figure 4 is'a transverse sectional vview taken on line 4-4 ofFigure 3; t

Figure 5 is an enlarged detail sectional view taken on the plane of Figure 2 showing the construction of the clutching mechanism;

from a driving member to a driven member wherein first and second gears are connected to the driving member and the driven member, respectively, and in which intermediate gears individually engage each of the first and second gears to provide a multiple power flow path be tween the driving and driven members.

It is another object of my invention to provide a power transmitting mechanism according to the preceding objects in which one of a plurality of gears of a closed gear train is mounted to provide for a floating movement of the same with respect to the other gears.

In carrying forth the foregoing objects, I have provided a transmission assembly having a housing within which is rotatably mounted a pair of juxtaposed idling gears, said gears being adapted to be selectively clutched to a concentrically mounted cross shaft. A power input pinion is drivably engaged with each of the aforementioned idling gears and is operatively connected by means of a double universal joint, or the like, to a transmission power input shaft. This power input pinion may be mounted upon an arm of a yoke member which encircles the transverse cross shaft. The yoke may be adapted to 'be rotatably oscillated within the housing thereby permitting the power input pinion to move in a direction substantially transverse to its central axis.

A power output gear is also drivably engaged with each of the two idler gears and is rotatably mounted in a juxtaposed-position with respect to the power input pinion.

During the operation of the transmission, the power output pinion is permitted to automatically adjust itself so that compensation takes place for the backlash which exists in the closed gear path. Thus, two paths are provided for the delivery of power from the driving power vinput member to the power output member, each of the idler gears respectively forming a portion of one of the paths. r

Figure 6 is a partial sectional view showing the relative position of the input bevel gear; and

Figure 7 is a schematic representation of a second embodiment of my invention wherein the power output shaft and the power input shaft are in substantially parallel relationship.

' Referringfirst to Figures 1, 2 and 3, the transmission housing is generally designated by means of numeral 1. A power input flange 2 may be integrally formed on one end of a power input shaft 3, as shown. Flange 2 may be drivably coupled to a suitable power shaft or drive shaft, not shown. The power input shaft 3 is splined to the end hub 4 of a double universal joint coupling which may best be viewed in Figures 2 and 3. The input shaft 3. is rotatably mounted within an end portion of the housing 1 by means of suitable bearings 5.

- The end hub 4 is bolted securely by means of bolts 8 to universal joint caps 6 and 7 which are mounted upon a diametrically opposed pair of the four equally spaced radial studs on the universal joint spider member 9. The caps 6 and 7 are free to undergo angular movement about the axis of the studs upon which they are mounted. Another pair of caps 10 and 11 are similarly mounted on the two remaining studs of the spider member 9, as shown.

Caps 10 and 11 may be securely bolted to a universal joint centerplate 12 which provides a support upon which other universal joint caps 13 and 14 are bolted. Caps 13 and 14 are situated on one face of the centerplate 12 while the caps 10 and 11 are situated on the opposite face.

The caps 13 and 14 are rotatably mounted on two diametrically opposed radial studs which are integral with a second spider member 15. Like the previously described universal joint caps 6, 7, 9, and 10, the caps 13 and 14 are free to undergo angular deflection with-respect to the axis of the studs upon which they are mounted. The two remaining studs of the spider member 15 are adapted to rotatably support another pair of universal joint caps 16 and 17 which in. turn are bolted securelyto an adaptor plate shown at 18.' This adapter plate -18 has a central hub which is internally splined to an extended hub 20 of the input bevel gear 19. The bevel gear 19; adaptor plate lS; andcaps 16 and 17 thus comprise a unitary, rotatable assembly;

The input bevel gear l-9- is free to-movein a -verti'cal plane,- while simultaneously rotatin-g about its own axis. It-is possible-for the axis of the input shaft to-form an angle with respectto -a -horiz'ontal reference line which is of a diiferent magnitude than the angle formed *by the axis of r the input bevel gear -19' with the-same reference line. Further, it is not necessary-that the' -axis'of the input-bevel gear-19 and the axis of the -.input-=shaft-3 should intersect. Because ofth'e freedomofmoti'onof this input'bevel gear it mav-be appropriately termed a floating? pinion.-

A yok'eis shown at-21 and'it -is slidably supported" by a--cylindrica-l -.shell 22 which in -turn -is" supported bypa, rallel web portions 23 and 24. These w'eb'portions form extensions of the outer housing casting {and are-integral with'the same. In-this presently disclosedembodiment; the shell 22 is secured to the two-web portions 231-and 24 by means-of-a press fit. As'best seen in FigureZ; the yoke 21 includesan extended-arm 25 uponwhich;,the input bevel: gear- 19 i is rotatably zmounted f by means of bearings 26. 7

As best seen in Figure 2, two idler'beveljgearsar'e shown at 27' and 28 which'are provided with extended hub portions 29 and- 30,-respectively. An external spline 31' is formed on one .end of the hub portion 29 and a similar external spline 32' is formed on the hub'p'ortion 30." The idler gear 27, is rotatably .mounted withir'itli' liousingb'y means' of suitable bearings '33 a'ndj34 located at opposed ends of the hub portion-29." Bearingi33' is backed up and secured by the cylindrical shell 22whichlin turn is firmly supported by web portions 23'and24, as previous: ly described. Bearing 34 is backed'up by and secured within the outer housing casting 1, as. shown. Idler gear 281s: similarly mounted by means of bearings 35 and'36,"bearing 35 being secured by the cylindrical shell 22 and bearing 36v beingsecured by the outer housing 1.

A power output bevel,- gear is shown at 37 in Figures 2, 3, and 6, said bevel, gear 37 being drivably engagedby the two idler gears 27 and 28. This output gear .37 is rotatably mounted upon two. suitable bearings 38 and 39 situated at either end. of;a.centralgeanhub on opposed sides of the gear proper. The;bearing-38 is secured by the web portions 23 and '24 andthe bearing 39;is secured by the transmission housingl.

A hollow cross shaft 40may beconcentrically mounted with respect to thetwo idler bevel;gear,s,27 and 28 and it extendsthrough the.transmissionassembly perpendicularly with respect to thepower input: shaft 3. Two flanges 41 and 42 may be secured to-either-end of the'cross shaft 40 on the exterior of the,transmissionhousing 1. The sub-assembly consisting of the cross: shaft 40, and the two flanges 41 and 42 is end-supportedcibytwo axially spaced bearings 43 and 44,. which';. in :.turn aremountedin the outer housing 1. The two idler bevel gears 27 and-.28 are independently revolvable upon-the power.; output'shaft 40.4 Oil seals may be provided ,asashowngatthe-'basewf each of the flanges 41 and .42 andlalsozat the base of :the power input flange '2 as shown.

As previously described, in .myucopending application, mentioned above, the bevel gears 27 and 28 maybe adapted :to function as power output gear'sand are effective to transmitpowertothescross1shaftg40iandthe associatedflangesfll and 42: Forthe purpose of seleetively clutching either of th,e;-ge ars:27'or.28vto:;the =shaft' 40, a clutching H'lBChQHiSmylSPIQVidCd:. This mechanism has beendescribed-in my copending-application-and it lS,.fiCtiV6ttOr selectively provide-*a-positive driving engagement :between-w either of t'he gea'rs 27' oi s28 and thevshaft: ;40Jwhen. .a'ppwem absorbing means isteoupled to either or both of the flanges and 42. However, this clutching mechanism is not an essential component of my present invention as herein disclosed. I contemplate that the clutching mechanism may be moved to an inoperative or neutral position while carrying out the principles of my instantinvention, the gears 27 and 28 thereby being permitted to function solely as idler gears.

Althoughtheclutehing mechanism isnotprcsently re.- quired; as above mentioned; certain features-thereof will be set forth in my instant disclosure for thepurpose of providing a more, complete description of the transmission structure.-

A; shifting lever. 46" is splinedyto, a rotatable shaft v47 which is positively secured to a shifting fork:42',as:best seen in Figure 3. The tworextremities of the shifting for 48 have mounted thereomshoes 49wh'ich are situated inside a peripheral groove 45 located in an internally spline'd: shifter element 50: Anin-termediate'portion 51 ofthe output shaft 40 isexternally splinedand-is adapted to' mesh with the iinternally-'splined shifter-element 50 Rotary-motion may be imparted to the shifting for 481and=thesh aft 47 by-the -lever 46,- the shifter element 50 thereby being moved in either axial direction along the spline'd intermediate "portion-51 of the shaft 40.

A hollow-- tube 52 isembeddedat one end thereof in the housing -1 audit acts asa-carr'tilever supportfor the shaft 47, the shaft 47 being assembled concentrically with respect to the -tube-523 To avoid interference-with-tube 52, yoke 21'and'the'cylind-rical'Shelli-22 are-cut away as shown,- to-produce aslo't 55 through-which-tube-SZ extends;

As best seen in Figure 5, the shifter element SO'may be =rnoved-toeither of three-operating positions whichare identifid'as position-'1, position 2, and position'3; When the "shifting fork: 48"- causes" the shifter" element 50 to assume position 2'; the" bevelgear 27 becomes positively clutchedtoshaft"40 and it functions asxa' power output gear, the shaft 40 being driven in one" direction. When the shifting element is moved-to-position 3; the bevel gear 28 -'fu'nctions as -the-poweroutput gear andthe shaft 40 is driven inthe-opposite direction.

I 'presently;-contemplate thatthe bevelgear 37may function asa power output gear'and I have therefore provided the-same with -an extended hub portion which is internally splined" as'shown at 53. A suitable externally splined-power-output'shaft-54 may be drivably engaged-with thisin'ternally' splinedhubportion of output gear 371.

In thewp'eration of my present invention, the power input bevel gear- 19m'ay be rotatedcontinually in one direction by virtueof the above described closed coupled double universal.jointiinterposed between the power input=shaft*'3 andthe-gear 19. It will be assumed that the shifter-element 50is'moved by the shifting mechanism to theintermediateor-neutral position 1; as shown in Figure 5:

The power-input gear-'19-is drivably connected to the power output gear 37 "by each 'of theidler gears 27 and 28.

A backlashnormally exists between each of'the meshing-gears andthmragnitude of this backlash may vary betweencertain predetermined manufacturing tolerances. Accordinglyyit is-practically impossible to design the gears ofth'e-transmission--sothat the-sum of the backlash between gears 19 and"27"and-betweengears Hand 37 will be-exactly' equalto the sum ofithe backlash between gears 19 and l8 and between-gears -28-and 37. Compensation is made-for this inequality by the-floating characteristic of the power input gear--19.

For the"purpose=of-more particularly describing the operation-of my-instant-inventiom it will first be assumed that the power-input-gear is-rotatably'mounted in a, fixed positions The gearl9'may in this instancedrive gear'37 by virtue-ofthe'driving connection provided'by'idler gear 28 assuming'thatthe: sumof-th'e backlash' -betw'een gears 19 and 28.and-between gears 28 and 37v is less thatrthe sum of the backlash between gears 19 and 27 and between gears 27 and 37. If the sum is greater than the latter sum, then the output gear 37 will be driven by virtue of the driving connection provided by idler 27. It is thus seen that only one geared path is available for the delivery of power from the input shaft 3 to the power output gear 37.

If it is now assumed that the input bevel gear 19 is mounted to provide for floating movement as herein described, compensation for the difference in the sum of the backlash between the gears of the respective geared paths will take place. The power input bevel gear 19 will float until a driving engagement with the power output gear 37 is provided by each idler gear 27 and 28. Thus, two geared paths for the delivery of power are produced and the gear loads are accordingly reduced to approximately half the value of the gear loads which would exist if only a single power path were used.

In addition to the above, the gear loads are evenly balanced and are situated so that they tend to cancel each a other. The resulting bearing loads on each of the plurality of bearings herein described are therefore considerably reduced.

The free floating characteristic of the power input bevel gear 19 will also permit self positioning of the same and thereby prevent premature gear failure arising out of a zero backlash condition.

Although the power output shaft and the power input shaft for the transmission herein described are coaxially disposed, I contemplate that they may also be mounted in spaced and substantially parallel relationship. In this latter instance, the two shafts may be drivably connected by suitable gearing which is adapted to provide more than one power flow path and which may comprise either spur or helical gear elements or the like. Such an embodiment is illustrated schema-tically in Figure 7 wherein a power input shaft 3 is drivably connected to a power input pinion 14' by means of a double universal joint 4'. The pinion 14 is capable of limited oscillation about a transverse axis represented by a bearing shaft 21. The pinion 14' drivably engages idler pinions 27 and 28 which in turn are in driving engagement with power output gear 37', the latter being drivably connected to a power output shaft 54. The gear 37 and the pinions 27 and 28' may each be suitably journaled for rotation about their respective axes as illustrated.

What I claim and desire to secure by United States Letters Patent is:

1. In a power transmission for delivering power from a driving means to a driven means, a power input gear, a universal coupling means for drivably connecting said power input gear to said driving means, a power output gear drivably connected to said driven means, intermediate gears individually engaged with each of said power input and power output gears to form two power delivery geared paths, each of said gears having an axis of rotation, the axis of said intermediate gears being perpendicular to the axis of said power input and power output gears and means for mounting said power input gear to provide for limited displacement of the same in a direction which is substantially transverse to its axis of rotation thereby accommodating the simultaneous delivery of power from said driving means to said driven means through each of said geared paths.

2. In a power transmission, a power input driving means, a power output driven means, first and second power flow paths including gears drivably connecting said driving and said driven means, said paths including a common gear having an axis of rotation, each of said paths being adapted to simultaneously transfer power from said driving means to said driven means and each having the same number of gears, and means for rotatably mounting said comm-on gear to provide for limited displacement of the same in a direction substantially transverse to its axis of rotation as driving torque is applied thereto thereby substantially equalizing the amount of power being delivered through each of said paths.

3. In a power transmission, a power input driving means, a power output driven means, a plurality of power flow paths including gears drivably connecting said driving and said driven means, said paths including a common gear having an axis of rotation, each of said paths being adapted to simultaneously transfer power from said driving means to said driven means and each having one idler gear, and means for rotatably mounting one of said gears to provide for limited displacement of the same in a direction substantially transverse to its axis of rotation thereby substantially equalizing the amount of power being delivered through each of said paths.

References Cited in the file of this patent UNITED STATES PATENTS 2,161,702 Durig June 6, 1939 2,513,217 Tomlines June 27, 1950 2,560,865 Hindmarch July 17, 1951 FOREIGN PATENTS 633,971 Great Britain Dec. 30, 1949 

